EP3728824B1 - Amortisseur à bande large pour un moteur de véhicule automobile - Google Patents

Amortisseur à bande large pour un moteur de véhicule automobile Download PDF

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Publication number
EP3728824B1
EP3728824B1 EP18829324.5A EP18829324A EP3728824B1 EP 3728824 B1 EP3728824 B1 EP 3728824B1 EP 18829324 A EP18829324 A EP 18829324A EP 3728824 B1 EP3728824 B1 EP 3728824B1
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EP
European Patent Office
Prior art keywords
channel
pipe
broad
acoustic
housing
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Application number
EP18829324.5A
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German (de)
English (en)
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EP3728824A1 (fr
Inventor
Ralf Timme
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Montaplast GmbH
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Montaplast GmbH
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Publication of EP3728824A1 publication Critical patent/EP3728824A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1283—Manufacturing or assembly; Connectors; Fixations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1266—Intake silencers ; Sound modulation, transmission or amplification using resonance comprising multiple chambers or compartments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1277—Reinforcement of walls, e.g. with ribs or laminates; Walls having air gaps or additional sound damping layers
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/161—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general in systems with fluid flow
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1261—Helmholtz resonators

Definitions

  • the invention relates to a broadband resonance muffler, which is referred to below in simplified form as a broadband damper, in particular installed in an internal combustion engine, particularly preferably a motor vehicle engine, with an at least two-part housing, comprising in particular a lower housing shell and an upper housing shell.
  • the housing has a damper longitudinal axis and a damper transverse axis and accommodates a pipe carrying exhaust gas or gas which defines a pipe interior with a circumferentially surrounding pipe jacket with acoustic openings formed therein.
  • the pipe forming an air duct is enclosed in the installed position by at least one damping or resonance chamber formed by the housing, which is in operative connection with the pipe interior via the acoustic openings, and the housing comprises or is formed from two axially divided housing parts.
  • the increasingly quieter vehicles also pose a great challenge to engine technology, especially to its noise-intensive systems, which particularly affects the air intake system of the engine or a turbocharger of the same.
  • resonators are often used today.
  • a The resonator generally consists of one or more chambers which are connected to an intake line for air in a gas-permeable manner.
  • several resonators can be provided in different configurations, which compensate for different resonance ranges.
  • the housing with the tube arranged in it in the installed position form a damping system in the space between the inside tube and the outside housing, which extends along a system longitudinal axis or the damper longitudinal axis, which axis does not necessarily have to run along a straight line, but also curved or can be bent.
  • the individual damping chambers or resonance chambers are usually formed radially starting from the pipe at a distance from one another along the longitudinal direction of the damper of the overall system or the damping system formed in this way.
  • Such resonators are, for example, from DE 10 2010 022 780 B4 and EP 1 176 355 A2 known, as well as from the DE 10 2015 202851 A1 , US 2008 / 230307A1 and US 2005/284692 A1 .
  • the US 2006/032700 A1 describes a broadband resonance muffler with several resonance chambers, which are separated by partitions of a pipe insert body.
  • broadband resonance silencers of this type already enable extensive absorption of the undesired noises over a wide frequency spectrum, possibilities are still being sought to use them for even broader areas of application.
  • the invention is based on the object of at least partially avoiding the disadvantages indicated and in particular a noise damper or broadband resonance silencer for an internal combustion engine provide that enables or provides a particularly wide range of applications for many frequencies, which, even with a complicated geometry, takes up as little space as possible and is easy to manufacture.
  • the tube is designed as a tube insert body, i.e. as a preferably one-piece unit which comprises the tube or tube socket or a tube element that can be inserted into the housing parts in the installed position, the tube comprising several acoustic openings in the tube jacket surface and the Pipe insert body further comprises end connections for connection to adjacent pipes, lines or the like and at least one acoustic channel.
  • the at least one or each acoustic channel has at least one or exactly one channel inlet opening through which the fluid or gas flows into it and is closed at the end in order to function, for example, as a lambda / 4 channel or lambda / 2 channel.
  • the housing preferably comprises two parts, namely a first housing half-shell, in particular designed as a lower housing shell, as well as a second housing half-shell which can be placed on this and which is especially designed as an upper housing shell.
  • the damping chamber is in at least two via at least one insert web Divided into resonance chambers, the at least one insert web being formed in one piece with the insert body, and the insert web also functioning as a position fixing means.
  • the at least one acoustic channel comprises as a further feature an inlet opening which opens directly into the pipe.
  • the insert web and / or at least the duct inlet of the acoustic duct are thus also part of the preferably one-piece tubular insert body.
  • At least partial areas of the at least one or more acoustic ducts are also preferably parts of the preferably one-piece pipe insert body.
  • At least partial areas of the at least one or more acoustic ducts are particularly preferably part of the preferably one-piece tubular insert body and / or one or more complete acoustic ducts are part of the preferably one-piece raw insert body. If, in relation to a given acoustic channel, only a partial area of the same part of the preferably one-piece tubular insert body, the other partial area of the respective acoustic channel is preferably formed by the housing or one of the housing parts in order to complete it.
  • the respective “sub-area” of the acoustic channel is in each case a wall area of the acoustic channel, including the wall area closing the channel end opposite the channel inlet opening.
  • the partial areas of a wall of an acoustic channel, which are formed by the pipe insert body and a housing part on the other hand, are preferably welded to one another.
  • the broadband resonance muffler has a particularly simple construction and is particularly easy to manufacture, namely by inserting the tubular insert into one of the housing parts and closing or joining the preferably 2-part housing.
  • the broadband resonance silencer has improved sound absorption, since this comprises a broadband resonator and at the same time acoustic channels for additional and particularly effective damping of special frequencies, with both damping functions being integrated on the tubular insert body.
  • the invention thus provides a solution to the problem of providing, in addition to broadband damping by means of the at least one or more damping chambers, compensation for at least one or different frequencies by the at least one or more acoustic channels of different lengths and different geometries in a particularly small installation space, in order to at least to compensate or absorb one or different additional frequency ranges in the different acoustic channels corresponding to the frequencies, whereby the specific geometric configuration of an acoustic channel or several acoustic channels, e.g. in length and diameter, can be determined by a person skilled in the art adapted to the frequencies to be compensated.
  • noises can be compensated for in any large frequency range by appropriately designing the acoustic channel or several acoustic channels, in addition to broadband attenuation.
  • Preferred frequency ranges are between 200 to 800 Hz, but other frequency ranges are also quite possible.
  • a specific acoustic channel can be designed for the range of 200 Hz, an adjoining or separate acoustic channel for the frequency range of 300 Hz and another acoustic channel for the frequency range from 400 to 600 Hz or even up to 800 Hz.
  • the acoustic channels have different lengths and geometries in order to be able to intercept or compensate for the different frequency ranges.
  • the damping chamber can be provided with at least one insert web be subdivided into several resonance chambers or sub-chambers which are arranged one behind the other, for example, extending along the longitudinal axis of the damper.
  • the respective insert web thus acts as a partition to separate the adjacent resonance chambers from one another.
  • the separation of the resonance chambers by the respective insert web is in each case at least essentially gas-tight, with a low leakage rate in terms of gas exchange between adjacent resonance chambers being acceptable, provided that this does not significantly impair the noise-damping function of the respective resonance chamber.
  • the respective insert web is preferably fastened to the tubular insert body or, particularly preferably, is integrally formed thereon.
  • the broadband resonance silencer designed as an air duct system thus has two essential components, namely the external or receiving housing and the tubular insert body that can be inserted into it.
  • the tube insert body comprises the tube which guides the fluid or the air from a damper inlet side to a damper outlet side.
  • the broadband resonance silencer comprises the further at least one acoustic channel and insert webs for separating the resonance chambers from the housing shells and the tubular insert body, whereby the broadband resonance silencer is particularly easy to manufacture.
  • the broadband resonance muffler can be adapted to different requirements of the sound absorption, for example different configurations of a turbocharger, precisely by different arrangement of the insert webs and / or different configurations of the at least one or more acoustic channels.
  • the housing can thus consist of There are more than two partial housing shells, the term “housing half-shell” also being used for the sake of clarity instead of the term “partial housing shell”. In particular, however, the term “housing half-shell” should be referred to a two-part housing with two housing half-shells.
  • the housing which is thus preferably two-part, is preferably shell-shaped and preferably comprises a lower housing shell and an upper housing shell, which can be connected to one another, for example welded, at a separation point or separation plane, which preferably extends along the longitudinal axis of the damper.
  • the tubular insert body with the at least one insert web extending transversely to the longitudinal axis of the damper and at least the partial areas of at least one or more acoustic ducts is preferably designed in one piece, which is particularly advantageous in terms of production technology and handling when assembling the broadband resonance muffler.
  • the raw insert body can also be designed in several parts, provided that the individual sub-areas of the same are joined together to form a coherent group of components, so that the tubular insert body can be handled as one component and inserted into the housing shell, so that the broadband module can then be joined to the second housing shell. Resonance muffler can be produced.
  • the housing parts or housing shells are preferably manufactured by injection molding and are connected to one another in a sealing or gas-tight manner by means of welding.
  • the tube insert body with the air duct or tube that can be inserted and received in the housing is open at both ends and has one for the cross-section required for the media flow.
  • the volume or the interior of the housing formed between the housing and the pipe or air duct forms the broadband resonator, which can also be designed as a "Helmholtz resonator", which can comprise several sub-chambers or resonance chambers to compensate or cover the widest possible frequency spectrum which is subdivided by insert webs or insert walls provided on the insert body.
  • the seal required for the function between the resonance chambers preferably one behind the other in the longitudinal direction, can be implemented, for example, by a tongue and groove connection.
  • At least one groove is preferably formed on the inside of the housing, into which the at least one insert web, which functions as a partition between the resonator chambers, can be inserted.
  • the at least one acoustic channel forms a further tubular resonance volume, which can be designed as a quarter-wave resonator, for example.
  • the acoustic channel is preferably at least partially or completely formed by at least one channel wall which is formed on the outside of the pipe and which is preferably part of the pipe insert body.
  • the acoustic channel preferably starts directly from the pipe in each case.
  • the duct wall of the acoustic duct is preferably arranged on the outside of the pipe insert body and is preferably formed in one piece on the pipe insert body.
  • the duct wall can extend in the longitudinal direction of the damper in relation to the longitudinal direction of the duct, as a result of which the duct length can vary over larger areas and thus can cover individual frequencies of a larger frequency spectrum.
  • the duct wall can also extend transversely to the longitudinal direction of the damper, as a result of which the geometry of the duct extension can be varied over larger areas.
  • the at least one acoustic channel has a section extending with its longitudinal extension in the direction of the damper longitudinal axis and a section extending with its longitudinal extension along the damper transverse axis, so that the channel length and thus also the frequency detected by the channel is selected from a broad frequency range and the Damper can be adapted to different requirements.
  • the acoustic duct can extend at least in sections at a distance from the pipe jacket, forming a space between the duct and the pipe.
  • the geometry of the longitudinal extension of the channel can practically be freely selected and the channel length can vary over a wide range and be adapted to the respective requirements.
  • the tube of the tube insert has a plurality of acoustic openings, it being possible for a plurality of acoustic openings to be provided on the tube in each case for a resonance chamber.
  • the resonance chamber is formed between the tube and the housing, with adjacent resonance chambers being separated from one another by the insert webs.
  • several acoustic openings are provided on the pipe, which are arranged distributed around the pipe circumference and / or several acoustic openings (preferably more than two), which are arranged at a distance from one another in the longitudinal direction of the pipe.
  • the number and / or size of the acoustic openings, that is, their length, width and diameter, are individual for each chamber according to the desired frequency ranges to be damped Voted.
  • the at least one acoustic channel can also extend over several resonance chambers, it being possible for it to have any desired geometries.
  • the at least one acoustic channel preferably extends along the longitudinal axis of the damper and / or along the transverse damper axis, in particular in the edge-side area near or adjacent to the surrounding housing.
  • the acoustic channel preferably runs circumferentially along the edge of the pipe insert body, that is to say essentially reproduces the edge contour of the pipe insert body with a spacing.
  • the at least one acoustic channel has any desired geometry for the respective application, e.g. the geometry of a screw or spiral for particularly long acoustic channels.
  • the acoustic channel comprises at least one channel wall, channel rib or the like formed radially from the pipe insert body, in particular integrally formed thereon, which can be connected to the adjacent housing part in the installed position to form the acoustic channel, in particular by means of a tight connection to close the Acoustic channel.
  • This connection is preferably made by means of gluing, welding or the like.
  • the tubular insert body only has to be inserted into the one housing shell with the partition wall positioned and then closed with the second housing shell.
  • the tubular insert body is particularly easy to manufacture as a result, in particular also as an injection-molded component, in particular also as a one-piece component.
  • the channel wall can on the inside also in a correspondingly designed one Engage the groove on the inside of the housing.
  • Embodiments include that the channel wall can additionally be welded for sealing.
  • a corresponding plurality of acoustic channels or resonator channels can thus easily be provided in the given space by means of a plurality of channel walls, in particular running parallel next to one another.
  • the at least one or the respective acoustic channels or resonator channels each have at least one or exactly one channel opening or channel inlet opening through which an air flow or sound wave from the pipe can enter the respective channel, and is / are in each case at the opposite of the channel inlet End closed at the end.
  • the design of the channel opening as an elongated hole has proven to be particularly expedient, the inlet opening basically corresponding to the cross section of the acoustic channel.
  • the cross section and length of the acoustic channel are adapted to the frequency to be compensated.
  • the acoustic channels can be designed, for example, as an A / 4 (quarter-wave) channel or resonator or an A / 2 (half-lambda) channel or resonator.
  • the acoustic channel has 1 ⁇ 4 of the wavelength to be attenuated, so that when a sound wave passes to the end of the channel and back, the result is A / 4. Since the covered sound frequencies depend on the respective length of the acoustic channel, the acoustic channels thus formed can have different lengths.
  • the outer acoustic channels which therefore extend closer to the housing wall, are preferably designed to be larger, that is to say have a greater length, because they are relatively further away from the tube of the insert body.
  • Embodiments include the formation of the acoustic channel adjacent to the outer jacket surface of the pipe, but also at a distance from this outer jacket surface, so that they do not have to be in direct contact with the pipe jacket surface.
  • the configuration according to the invention offers weight and cost savings as well as a significant simplification of the manufacturing process.
  • the broadband resonance muffler according to the invention is preferably made of plastic and is preferably manufactured using an injection molding process, that is to say designed as a multi-part injection-molded part.
  • the broadband resonance silencer thus comprises several, preferably two, housing parts that can be connected to one another at a joint to form an interior space, in particular designed as housing half-shells, which can be separated in the transverse direction of the system, i.e. radially, and between them the gas-carrying pipe with an inlet and an outlet end at the front ends as well as several acoustic openings in the pipe jacket.
  • the at least one acoustic channel is formed by a between the outer circumferential surface of the tubular insert body and the housing that encloses or encloses it in the installed position, in particular a continuous channel wall, which is preferably formed in one piece on the outside of the tubular insert body as a protruding web, which in the installed position through the inner surface or wall of the housing is closed.
  • the at least one channel wall is preferably formed on the pipe insert body, for example molded in one piece on it.
  • the design is reversed, i.e. the channel wall is formed on the inner surface of the housing or the housing parts, which then rests in the installed position on the outer surface of the pipe insert body and thus defines the circumferential acoustic channel.
  • embodiments include several such channel walls which are formed offset from one another on the outer surface between the tube insert body and the housing and which thus act for different resonance areas.
  • These acoustic channels thus formed by the channel walls thus form further individual acoustic chambers, which can therefore be designed as desired for the noises to be influenced or for the vibrations to be compensated.
  • Embodiments include at least one partition or duct partition or boundary walls arranged in the acoustic duct or ducts, which can limit the duct length as required to compensate for certain frequencies. These channel dividing or delimiting walls can also be designed to be plugged in at a later date, for example in the form of a tongue and groove connection between the two joining partners.
  • embodiments provide different acoustic channels in different planes, which can be connected to one another via a connecting channel, for example acoustic channels formed below or above one another in the longitudinal direction of the damper.
  • Embodiments provide for the acoustic channels to be designed at different levels offset in height relative to the central longitudinal axis of the damping system, preferably designed as circumferential closed damping or acoustic channels.
  • the damping system consists of a housing and a tubular insert body.
  • the individual acoustic channels preferably extend essentially transversely to the longitudinal direction of the system and are preferably formed circumferentially, e.g. essentially extending in one plane, on the pipe insert body, although individual acoustic channels can be formed on different levels on the pipe insert body.
  • a first, and thus upper acoustic channel in the installed position can comprise an acoustic channel formed on the upper side of the pipe insert body, which opens into a second, lower acoustic channel via a connecting channel that extends downwards, in particular transversely to the longitudinal direction of the system, which is formed, for example, circumferentially on the outer edge of the pipe insert body .
  • an acoustic channel can also comprise a blind hole which extends vertically downwards or upwards or from a first acoustic channel to a second acoustic channel which is offset in height in relation to this first acoustic channel, this preferably being essentially transverse to the direction of longitudinal extent extends.
  • This blind hole can function as a connecting channel between two acoustic channels or acoustic channel subsections, which are e.g. formed on different levels in the broadband resonator. Even further differentiation or frequency absorption in a small space can be achieved if an acoustic channel or a further acoustic channel is formed in at least one connection area of a pipe end.
  • This acoustic channel is preferably designed as a circular annular space, which is particularly preferably designed in or on a pipe connection of the broadband resonance muffler.
  • This pipe connection is particularly preferably formed in one piece on the housing.
  • Embodiments provide for position fixing means formed between the joining partners, i.e. the insert body and the housing, e.g. in the form of insert webs on a joining partner which, in the installed position, engage in grooves on the inside on the corresponding other joining partner and which thus ensure a more precise positioning of the insert body in the housing.
  • the webs can, for example, be designed in the form of plates which are fixed to the insert body, preferably formed in one piece on this.
  • the position fixing means between the insert web and the housing also prevent the webs from vibrating during operation of the damper.
  • the insert webs are at least essentially gas-tight with the inside of the housing.
  • the "installation position" as well as generally within the scope of the invention, relates in each case to the position of the respective component in the broadband resonance silencer that is ready for use.
  • the broadband resonance muffler preferably comprises one Pipe connection on the inlet side in the direction of flow and a pipe connection on the outlet side in the direction of flow for connection to the media-carrying lines.
  • These pipe connections are preferably formed on the housing, specifically as circular connection pieces on which the connection pipes can be placed.
  • inlet openings can be formed in the tubular surface of the insert body.
  • the respective acoustic channel thus has an inlet opening at its inlet end which is formed in the tube jacket surface of the tube of the insert body.
  • the acoustic channel thus connects directly to the tube of the tube insert body.
  • the acoustic channel goes with its channel wall directly from the pipe.
  • the at least one or more inlet openings can in particular be designed as elongated holes and are preferably adapted to the size of the acoustic channel, that is to say approximately as large as the cross section of the associated acoustic channel.
  • the respective acoustic channel is designed to be closed at its end opposite the inlet opening, so that the sound wave entering the channel is reflected back into the pipe at the channel end.
  • the channel is thus designed in the manner of a lambda / 4 signal.
  • the acoustic channel thus has a closed and uninterrupted side wall over its entire length, which is at least essentially or practically completely gas-tight, except for the inlet opening of the channel. If the duct wall is formed by two components, for example the pipe insert body and the housing or a housing part, then these components are at least essentially joined together in a gas-tight manner, particularly preferably welded.
  • Embodiments provide for an acoustic channel to be subdivided into two acoustic channel sections by at least one partition wall extending transversely to the longitudinal axis of this acoustic channel.
  • These partition walls can preferably be used for particularly simple adaptation to the respective application, i.e. for simple adaptation of the length of the acoustic channel at different points so that they can be connected to the acoustic channel, e.g. can be used to compensate for different frequencies.
  • the broadband resonance silencer according to the invention is preferably arranged between a turbocharger and an air filter housing of an internal combustion engine in order to compensate for undesired resonances.
  • the invention relates to an internal combustion engine with a broadband resonance silencer described above.
  • connection In the context of this description, the terms “connected”, “connected” and “integrated” are used to describe both a direct and an indirect connection, a direct or indirect connection and a direct or indirect integration.
  • identical or similar elements are provided with identical reference symbols, insofar as this is appropriate.
  • the broadband resonance muffler essentially comprises a two-part housing 2 designed as a plastic injection-molded part, designed for inserting or receiving the tubular insert body 4.
  • the housing can optionally also consist of more than two half-shells.
  • the broadband resonance muffler comprises a two-part housing 2, which has a longitudinal damper axis and a transverse damper axis, an exhaust gas or gas-carrying pipe 4.1 accommodated in the housing, which defines a pipe interior with a circumferentially surrounding pipe jacket with acoustic openings formed therein, with the pipe 4.1 is enclosed in the installed position by at least one damping chamber formed by the housing, which is in operative connection with the pipe interior via the acoustic openings 4.2.
  • the housing 2 in the present case comprises two housing parts designed as two housing half-shells 2.1, 2.4.
  • the tube 4.1 is designed as a tube insert body 4 in all embodiments, which comprises a central tube section with two frontal tube ends.
  • the insert body 4 is in the housing parts of the Housing designed to be used and the broadband resonance muffler has at least one acoustic channel 2.6, 4.5, 4.6, 4.13, 4.15, 4.20.
  • the damping chamber is subdivided into at least two resonance chambers via at least one insert web 4.3 and the at least one insert web 4.3 is formed integrally with the insert body 4.
  • the insert web 4.3 also functions as a positional fixing means.
  • the at least one acoustic channel comprises an inlet opening (4.11, 4.12) which is formed in the tubular insert body.
  • the housing 2 comprises an essentially trough-shaped lower housing shell 2.1 with a central receiving area for receiving the pipe insert body 4, into which the pipe insert body 4 can be inserted in such a way that the frontal pipe ends of the pipe 4.1 of the pipe insert body 4 with the socket-shaped and one-piece pipe connections 2.2, 2.3 the lower housing shell 2.1 complete.
  • the lower housing shell 2.1 can be closed media-tight via a roof-shaped upper housing shell 2.4, for which the lower housing shell 2.1 has a circumferential, closed insertion groove 2.5 in the outer edge area, into which a complementary sealing web on the upper housing shell 2.4 engages in a media-tight manner in the installed position.
  • the tube insert body 4 thus comprises a central tube 4.1, which extends along the longitudinal axis and which comprises an outer tube jacket surface in which several acoustic openings 4.2 (only one provided with a reference number) are distributed circumferentially at different points.
  • the tube insert body 4 comprises at the lower end in FIG Radially protruding insert webs 4.3 which are spaced apart in the longitudinal direction and extend transversely to the longitudinal direction of the system (only one labeled with a reference number), which in the installed position can be inserted into insertion grooves 2.5 (only one labeled with a reference number) provided on the inside of the lower housing shell 2.1.
  • Two acoustic channels 4.5, 4.6 are formed on the upper side of the tube insert body, namely an outer acoustic channel 4.5 and an inner acoustic channel 4.6, which are formed by channel walls 4.7, 4.8 projecting in one piece on the outside of the tube 4.1 of the tube insert body 4, which protrude towards the outer edge of the tube insert body 4 extend circumferentially at a distance from one another so that the circumferential acoustic channels 4.5, 4.6 are formed between these and the surrounding housing 2 at a radial distance from one another, which in the present case have approximately the same width, of which the inner acoustic channel is, however, correspondingly shorter.
  • the pipe insert body comprises 4 So at the proximal input end on the right in the figures, input openings 4.11, 4.12 designed as elongated holes 2.7 for the acoustic channels, through which the medium can enter the respective acoustic channel 4.5, 4.6 and exit again from the pipe interior.
  • circumferentially encircling acoustic channels 2.6 can be formed in pipe connections 2.2, 2.3, which therefore form a pipe connection 2.2.
  • Form circumferentially surrounding annular space which is formed on the inside by the pipe connection 2.2, in which an inlet opening also designed as an elongated hole 2.7 is provided, and on the outside by a ring attachment 6, which can be snapped onto the pipe connections 2.3, 2.4 so that between the Ring attachment 6 and the pipe connection 2.2, 2.3 around the pipe connections 2.2, 2.3 further acoustic channels can be formed.
  • a partition 2.8 pushed into this acoustic channel 2.6 and extending transversely to the longitudinal direction of the acoustic channel limits the length of the acoustic channel 2.6.
  • one circumferential acoustic channel 4.15 is also formed on the outer jacket surface of the pipe insert body 4.
  • this is designed in two parts and comprises two inlet openings in the form of elongated holes 4.16, 4.17, which are separated from one another by an insertable partition wall 4.18 at the inlet end and are separated from one another by a further partition 4.19 at the end. That way, the one in the Figure 7 lower acoustic channel section of acoustic channel 4.15 but only about half as long as in the Figure 7 upper acoustic duct section of the acoustic duct 4.15. By repositioning the partition wall 4.19 at different points, this tubular insert body 4 can be adapted particularly easily to different frequency ranges.
  • FIG. 8 shows an isometric top view of an embodiment of a broadband resonance silencer with an acoustic channel 4.20 which is partially formed on two levels and which in turn comprises several acoustic channel subsections.
  • the visible upper levels of the two acoustic duct sections each have an associated inlet opening designed as an elongated hole 4.21, 4.22 and a partition 4.23 arranged between them. These acoustic duct subsections are in turn bounded by a partition wall 4.24 ending the two subsections.
  • this embodiment comprises a schematically indicated blind hole 4.25 that extends vertically, ie transversely to the direction of longitudinal extent, which represents an extension to compensate for further frequencies.
  • this blind hole can be fluidically connected to a concealed acoustic duct section arranged underneath, which enables further design options for frequency compensation in an extremely limited installation space.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Manufacturing & Machinery (AREA)
  • Exhaust Silencers (AREA)

Claims (17)

  1. Amortisseur résonant à large bande, comprenant au moins un boîtier (2) en deux parties définissant un axe longitudinal de l'amortisseur et un axe transversal de l'amortisseur, un tube (4.1) reçu dans le boîtier et conduisant les gaz d'échappement ou les gaz, tube qui définit un intérieur de tube avec une enveloppe de tube périphérique dans laquelle sont formées des ouvertures acoustiques, dans lequel le tube (4.1) dans la position installée est entouré par au moins une chambre d'amortissement qui est formée par le boîtier et qui est reliée de manière opérationnelle à l'intérieur du tube via lesdites ouvertures acoustiques (4.2) afin de former un résonateur à large bande, dans lequel le boîtier (2) comprend au moins deux parties de boîtier, en particulier deux demi-coques de boîtier fendues (2.1., 2.4), dans lequel le tube (4.1) est conçu comme un corps d'insertion de tube (4) qui comprend une section de tube centrale avec deux extrémités de tube frontales, le corps d'insertion de tube (4) étant conçu pour être inséré dans les parties de boîtier du boîtier (2), dans lequel la chambre d'amortissement est divisée en au moins deux chambres de résonance par au moins une nervure d'insertion (4.3), le résonateur à large bande pouvant également être conçu comme un résonateur de Helmholtz, dans lequel au moins une nervure d'insertion (4.3) sur le corps d'insertion (4) est formée d'un seul tenant avec celui-ci, dans lequel la nervure d'insertion (4.3) servant en outre de moyen de fixation de position du corps d'insertion de tube par rapport au boîtier, dans lequel au moins un canal acoustique (4,5, 4.6, 4.11, 4.12, 4.13, 4.15, 4.20) formant un volume de résonateur tubulaire étant inclus en plus du résonateur à large bande, l'ouverture d'entrée (4.11, 4.12) du canal acoustique étant formée dans le corps d'insertion de tube, caractérisé en ce que
    i) le canal acoustique s'étend, au moins par sections, espacé de l'enveloppe de tube tout en formant un espace intermédiaire entre le canal (4,5, 4.6, 4.11, 4.12, 4.13, 4.15, 4.20) et le tube (4.1) et/ou
    ii) s'étend dans la direction de l'axe longitudinal de l'amortisseur sur plusieurs chambres d'amortissement.
  2. Amortisseur résonant à large bande selon la revendication 1, CARACTÉRISÉ EN CE QUE le canal acoustique (4.11, 4.12) s'étend avec son étendue longitudinale dans la direction de l'axe longitudinal de l'amortisseur, au moins par sections.
  3. Amortisseur résonant à large bande selon la revendication 1 ou 2, CARACTÉRISÉ EN CE QUE le canal acoustique (4.11, 4.12) s'étend avec son étendue longitudinale le long de l'axe transversal de l'amortisseur, au moins en sections.
  4. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 3, CARACTÉRISÉ EN CE QUE le canal acoustique (4.11, 4.12) est disposé à distance de l'enveloppe de tube dans une section de son extension longitudinale et/ou transversale.
  5. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 4, CARACTÉRISÉ EN CE QUE le canal acoustique (4.11, 4.12) est disposé sur la paroi intérieure du boîtier dans une section de son extension longitudinale et/ou transversale.
  6. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 5, CARACTÉRISÉ EN CE QUE l'au moins un canal acoustique s'étend dans la région du bord près ou adjacent au boîtier environnant.
  7. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 6, CARACTÉRISÉ EN CE QUE le canal acoustique a une extrémité opposée à l'ouverture d'entrée qui est au moins sensiblement fermée.
  8. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 7, CARACTÉRISÉ EN CE QUE le canal acoustique pénètre à travers au moins une nervure d'insertion (4.3) du corps d'insertion et est de préférence moulé d'un seul tenant avec ladite nervure d'insertion.
  9. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 8, CARACTÉRISÉ EN CE QU'au moins une section de paroi de canal du canal acoustique (4.5, 4.6) est formée par une sous-section du corps d'insertion de tube (4) et/ou une sous-section du boîtier (2).
  10. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 9, CARACTÉRISÉ EN CE QUE le canal acoustique fait partie du corps d'insertion au moins avec une sous-section de celui-ci.
  11. Amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 10, CARACTÉRISÉ EN CE QUE la paroi de canal du canal acoustique (4.7, 4.8) est formée avec une sous-section sur le corps d'insertion et avec une autre sous-section sur le boîtier (2), les deux sous-sections formant ensemble le canal acoustique respectif.
  12. Amortisseur résonant à large bande selon l'une quelconque des revendications précédentes, CARACTÉRISÉ EN CE QUE ladite au moins une paroi de canal (4.7., 4.8) est formée de manière circonférentielle sur le corps d'insertion de tube (4).
  13. Amortisseur résonant à large bande selon l'une quelconque des revendications précédentes, CARACTÉRISÉ EN CE QU'un autre canal acoustique (4.5, 4.6) est formé sur au moins un raccord de tuyau (2.2, 2.3).
  14. Amortisseur résonant à large bande selon l'une quelconque des revendications précédentes, CARACTÉRISÉ EN CE QUE l'ouverture d'entrée (4.11, 4.12) ou l'ouverture de canal est plus grande que les autres ouvertures acoustiques.
  15. Amortisseur résonant à large bande selon l'une quelconque des revendications précédentes, CARACTÉRISÉ EN CE QUE le canal acoustique (4.5, 4.6) comprend une paroi de séparation de canal (4.18, 4.19, 4.23, 4.24).
  16. Moteur ou turbocompresseur de moteur à combustion comprenant un amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 15 dans le système de guidage d'air, notamment le système d'admission d'air d'un tel moteur.
  17. Procédé d'amortissement du bruit utilisant un amortisseur résonant à large bande selon l'une quelconque des revendications 1 à 15 ou un moteur ou un turbocompresseur d'un moteur à combustion selon la revendication 16, dans lequel, en plus de l'amortissement à large bande, ledit au moins un ou chaque canal acoustique présente au moins une ou précisément une ouverture d'entrée de canal par laquelle le fluide ou le gaz s'écoule dans celui-ci et qui est fermée à l'extrémité afin de fonctionner comme un canal lambda/4 ou un canal lambda/2.
EP18829324.5A 2017-12-20 2018-12-18 Amortisseur à bande large pour un moteur de véhicule automobile Active EP3728824B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017130661.7A DE102017130661A1 (de) 2017-12-20 2017-12-20 Breitbanddämpfer für einen Kraftfahrzeug-Motor
PCT/EP2018/085587 WO2019121744A1 (fr) 2017-12-20 2018-12-18 Amortisseur à bande large pour un moteur de véhicule automobile

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EP3728824B1 true EP3728824B1 (fr) 2021-04-28

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US (1) US11434855B2 (fr)
EP (1) EP3728824B1 (fr)
CN (1) CN111512038B (fr)
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WO (1) WO2019121744A1 (fr)

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Publication number Publication date
CN111512038B (zh) 2022-06-14
EP3728824A1 (fr) 2020-10-28
WO2019121744A1 (fr) 2019-06-27
US20210293210A1 (en) 2021-09-23
DE102017130661A1 (de) 2019-06-27
CN111512038A (zh) 2020-08-07
US11434855B2 (en) 2022-09-06

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